Valve and control

ABSTRACT

A mechanically operated snap-action valve which is capable of functionally replacing a solenoid-controlled valve and of rapidly and precisely applying a source of air under pressure to a wide variety of pneumatic devices. The valve includes improved internal sealing arrangements and snap-action actuating mechanism responsive to actuating forces applied either manually or mechanically which actuating forces are of a relatively low order yet are capable of transferring a wide range of systems pressures with a high order of reliability and repeatability.

' 3,200,844 8/1965 .lack'son........... 137/6252 3,460,574 8/1969 Risher l37/625.21X

Primary Examiner-Henry T. Klinksiek Attorney-Amster & Rothstein ABSTRACT: A mechanically operated snap-action valve which is capable of functionally replacing a solenoid-controlled valve and of rapidly and precisely applying a source of air under pressure to a wide variety of pneumatic devices. The valve includes improved internal sealing arrangements and snap-action actuating mechanism responsive to actuating forces applied either manually or mechanically which actuating forces are of a relatively low order yet are capable of transferring a wide range of systems pressures with a high order of reliability and repeatability.

0 United States Patent [72] Inventor Alton K. Allen 11 Flower Lane, Kings Point, N.Y. 11024 [21] App]. No. 42,241 [22] Filed June 1, 1970 [45] Patented Nov. 9, 1971 [54] VALVE AND CONTROL 23 Claims, 15 Drawing Figs. 52 137/6251, 74/104, 74/527, 251/283, 277/194, 277/199 [51] Int.Cl..... ...................................................F16k11/02, Fl6k 39/04 [50] Field of 74/104, 527; 137/625.2,625.21; 251/283; 277/194, 199

[56] References Cited UNITED STATES PATENTS 2,653,003 9/1953 Overbeke..................... 137/625.2l

I a A h In 2 mm I ii Lm 4 i W a 7 4 1 Mm a 5 I.

PATENTED NOV 9:971

SHEET 1 BF 4 FIGS.

FIG. 4.

PATENTEUNUV 9l97l 3,618,635

FIG. 7.

FIGS.

mwsmon. ALTON A. ALLEA/ l7 rraRNEYS PATENTED NOV 9197! SHEET 3 OF 4 VALVE AND CONTROL The present invention relates generally to valves of the type employed in pneumatic transfer systems and, in particular, to a mechanically operated snap-action valve for the transfer of air pressure.

Numerous valves and controls are commercially available and characteristically include an internal movable valve body arranged to selectively port air under pressure from an appropriate source to a pneumatically operated device, such as a piston and cylinder. Various electrical, mechanical and electromechanical devices have been suggested for the control and actuation of such valves, one of the most common expedients being a solenoid control wherein an electrical signal operates a solenoid for the purposes of controlling the valve. Not only do pneumatic systems of this kind require an available electrical source in addition to the air source, but experience indicates that in pneumatic systems requiring repeated use over long periods of time, the solenoid may have to be replaced due to wear and/or imprecise functioning of the valve. Of course, such systems are inherently noisy. Further, there are installations where, apart from the availability of an electrical source, the presence of electrical controls is not desirable (i.e., the possibility of spark generation due to the presence of electrical components in an explosive-prone atmosphere).

It is also known in the art to employ mechanically actuated snap-action valves wherein valve actuation is achieved by loading and unloading opposed springs in alternation. Often, devices of this type do not produce the desired repeatability in operation and are frequently large and cumbersome, relatively expensive and not readily substituted for their electrically operated counterparts. Further, in mechanical systems of this kind, it is often necessary to impart relatively large actuating forces to the valve for achieving the valving function, with the attendant disadvantageous design limitation imposed by the necessity of establishing such relatively large actuating forces.

Broadly, it is an object of the present invention to provide an improved valve and control which obviates one or more of the aforesaid difficulties. Specifically, it is within the contemplation of the present invention to provide a mechanically operated snap-action valve which is capable of responding to relatively low-actuating forces, requires very little change in actuating force over a wide range of working pressures transferred by the valve, has a high order of reliability and repeatability and is capable of operation over prolonged periods of use without the need for adjustment, repair, or replacement.

It is a further object of the present invention to provide a mechanically controlled air valve which requires a relatively low order and substantially constant actuating force for the transfer of a wide range of working pressures, which has a relatively large capacity requiring small operating forces for comparatively large valve openings, which is of a construction capable of manufacture by mass production techniques at relatively low-unit cost and which is of a size such that it is readily substitutable for electrically operated valves (i.e., solenoid or microswitch controlled valves) in a wide variety of working environments.

In accordance with an illustrative embodiment demonstrating objects and features of the present invention, there is provided a valve which comprises a housing having an internal valve chamber. An elongated valve-actuating and inlet shaft extends through the chamber and is journaled in the housing for rotation about the shaft axis. A radially extending valve member is disposed within the chamber, is operatively connected to the shaft and oscillates between first and second porting positions in response to oscillating motion of the shaft. Means which include an axial bore through the shaft, a radial bore through the valve member. an entry port at one end of the shaft and a valve port at the radially extending face of the valve member, establishes an air passage through the shaft and valve member which terminates at the valve port. A stationary valve plate is mounted on the housing and includes first and second exit ports in angular spaced relation which open through the radially extending face of the valve plate. The radially extending faces of the valve member and the housing are in shear contact and establish an air seal in the first and second porting positions of the valve member. Actuating mechanisms are operatively connected to the shaft for oscillating the valve member between the first and second porting positions. Advantageously, the actuating mechanism is of the snap-action type which includes opposed actuating springs which are loaded and unloaded in alternation and which respond to relatively low-actuating forces for the purposes of imparting the necessary control motion to the valve member to achieve the porting functions of the valve.

Further objects, features and advantages of the present invention will be more fully appreciated by reference to the following illustrative embodiments of the present invention, when taken in conjunction with the accompanying drawings, wherein:

FIG. 1 is a front elevational view of a typical valve and snapaction actuating mechanism demonstrating objects and features of the present invention;

FIG. 2 is an end elevational view of the valve, taken from the left of FIG. 1 and showing the associated hose connections to a representative piston and cylinder, the latter being shown on a greatly reduced scale;

FIG. 3 is a perspective view, on an enlarged scale, of the internal mechanisms within the valve;

FIG. 4 is a transverse sectional view taken substantially along the line 4-4 of FIG. 9 and looking in the direction of the arrows, showing details of the air inlet, exhaust, and internal stationary valve plate;

FIG. 5 is a sectional view taken substantially along the line 5-5 in FIG. 9 and looking in the direction of the arrows showing the fluid transfer path for the valve when in the normal rest position of FIGS. 1 and 2;

FIG. 6 is a horizontal section of the valve taken substantially along the line 6-6 of FIG. 1, on an enlarged scale and looking in the direction of the arrows;

FIG. 7 is an enlarged view of a portion of FIG. 6 showing arrangement between the housing and the combined valve actuating and air inlet shaft;

FIG. 8 is a sectional view taken along an angularly extending plane identified by the line 8-8 in FIG. 5 and looking in the direction of the arrows to show details of the stationary valve plate within the housing and the associated oscillating valve member;

FIG. 9 is a sectional view taken substantially along the line 9-9 in FIG. 6 showing the internal valve mechanisms and the snap-action actuating mechanisms;

FIG. 10 is a fragmentary sectional view taken substantially along the line 10-10 of FIG. 6 and corresponding generally to the right side of FIG. 9, showing further details of the snapaction actuating mechanisms;

FIG. 11 is a view similar to FIG. 10 but on a reduced scale showing the snap-action actuating mechanisms in the immediate position of actuation from the normal rest position of FIG. 10 and prior to passing through the dead center position for the actuating mechanisms;

FIG. 12 is a view similar to FIG. 11 progressed to the point of the valve having been actuated into the operated position;

FIG. 13 is a view similar to FIG. 12, but with the valve in an intermediate position during return from the operated position to the normal rest position of FIG. 10;

FIG. l4is a sectional view taken substantially along the line 14-l4 of FIG. 9, with the full lines showing the latching or escapement mechanisms for the valve in the position corresponding to FIG. 10 and with the dotted lines showing the latching mechanism in the position corresponding to FIG. II; and

FIG. 15 is a sectional view similar to FIG. 14, with the full line showing the latching mechanisms in a position corresponding to FIG. 12 and the dotted lines showing the latching mechanisms in the position corresponding to FIG. 13.

Referring now to the drawings, and in particular to FIGS. 1 and 2, there is shown a typical mechanically operated snap-ac tion valve 20 constructed in accordance with the present invention which, for convenience in manufacture, includes a three-part housing 22 including an end or actuating housing section 24, an intermediate or valve housing section 26 and an end or air-transfer housing section .28, the sections being connected together in any appropriate fashion, as by bolts 30 (see FIGS. 4 and The outer face of the air-transfer housing section 28 is formed with four ports appropriately threaded for hose connections, namely air inlet port 32, exhaust port 34, a first working port 36 and a second working port 38 (see FIG. 2). In a typical installation, air under pressure is introduced by hose 40 attached to air with its port 32 for transfer in the normal rest position of the valve through the first working port 36 and its hose 42 and upon actuation of the valve to the second end port 38 and its hose 44. Thus, by connecting the hoses or lines 42, 44 to a conventional pneumatic device, such as the piston and cylinder assembly 46 (FIG. 2), the valve may be employed to selectively direct air from inlet hose 40 to one side or the other of the piston and cylinder assembly 46 and to appropriately port the other side of the assembly 46, as is generally understood. Of course, it is to be understood that this application is purely illustrative and numerous other uses are intended for the present mechanically controlled air valve.

As best seen in FIG. 9, the several ports 32, 34 36, 38 extend through the air-transfer housing section 28 and communicate with an internal valve chamber 48 formed within valve housing section 26. Disposed within the internal valve chamber 48 is a movable valve subassembly 50 shown in perspective in FIG. 3 in association with its internal actuating mechanisms 52. subassembly 50 includes an elongated valve actuating and inlet shaft 54 which is journaled at one end portion on end housing section 28 and on the opposite end portion on intermediate housing section 26 (see FIG. 6). The shaft 54 journals an oscillating internal valve head 56 of subassembly 50 within valve chamber 48. As seen in FIG. 6, the valve actuating and air inlet shaft 54 includes an elongated hollow section 54a defining passageway 54b which is journaled on section 28 and is in communication with the air inlet port 32 and a smaller diameter mounting section 54d which is journalcd on section 26 by thrust bearing 58. Mounting section 540 extends beyond the intermediate housing section 26 into the interior 60 of end housing section 24 where it carries the internal actuating mechanisms 52. Mounting of said shaft section 54a on housing section 28 is accomplished by the provision of a special bearing and sealing arrangement which includes a cylindrical bushing 62 which is seated on housing section 28 and provides an annular bearing contact for shaft section 540. inwardly of bushing 62 in the direction of air flow (see FIG. 7), there is disposed cooperating sealing members 64, 66 providing a metal-to-metal seal 68 at opposed radially extending faces. Sealing member 64 is provided with an annular inwardly opening seat which receives O-ring 70 which is compressed against the outer periphery of the shaft 54 such that sealing member 64 rotates with shaft 54. Similarly, sealing member 66 is provided with an annular outwardly opening seat which receives O-ring 72 which effectively maintains sealing member 66 in a stationary position as part of the surrounding housing section 26. The sealing assembly is completed by the provision of a spreadable thrust ring 74 which is snapped into an appropriate inwardly opening seat formed in housing section 26.

In use, it will be appreciated that chamber 48 is always vented to atmosphere through exhaust or discharge port 34 while the air inlet port 32 and the hollow interior 54b of shaft 54 are under line or working pressure. Such line pressure is applied against O-ring 70 due to the clearance between thrust or sleeve bearing 62 and sealing member 64 and is also applied to O-ring 72 due to that clearance and the further clearance between sealing member 64 and the housing section 28. Accordingly, line pressure urges the sealing members 64, 66

against thrust ring 74 (atmospheric pressure being at the side of sealing ring 66 facing thrust ring 74 through chamber 48). Accordingly, the line pressure seats the respective O-rings 70, 72 within the seats of the sealing members 64, 66. Effectively, sealing member 64 and O-ring 70 become a unitary assembly with shaft 54, while sealing member 66 and O-ring 72 become a unitary assembly with housing section 28 and a metal-tometal shear type face seal 68 is established by the annular contacting faces of sealing members 64, 66. As is generally un derstood, this shear-type face seal becomes more and more effective incident to wear. Inherently, the shear-type face seal 68, although highly effective in achieving the desired scaling function, does so with a very low level of friction such that there is very little frictional resistance introduced into the valve by the presence of seal 68.

The hollow interior 54b of shaft 54 communicates through cutout 54c (see FIG. 6) with a radially extending bore 56a which terminates at its outer end in a cylindrical well 5612 (see FIG. 8) which opens through the radially extending face of the oscillating head 56. Mounted within the well 56b is a sealing sleeve 76 which is biased outwardly relative to head 56 by coil spring 78 seated therebehind in well 56b. Surrounding the sealing sleeve 76 is an O-ring 81 which is seated in an appropriate annular grove formed in the oscillating valve head Sealing sleeve 76 includes a body 76a which terminates at its inner end in annular end face 76b against which spring 78 bears and at its outer end in a radially and outwardly offset annular sealing ring 76c which is biased against stationary sealing plate mounted on the adjacent inner face of air-transfer housing section 28 (see FIG. 4). The configuration of the sealing sleeve 76 contiguous to stationary sealing plate 80 is such as to provide an undercut at location 83 such that line pressure is effectively applied to opposite end faces 76b, 76d of the sealing sleeve 76. By appropriate selection of the design parameters for sealing sleeve 76, it is possible to substantially equalize the pressure on sealing sleeve 76 such that it will essentially float insofar as line or working pressure is concerned and is biased in the sealing direction by spring 78. Accordingly, the sealing force at the interface between sealing sleeve 76 and stationary sealing plate 80 can be established substantially independent of line pressure such that the desired sealing force may be established without introducing increasing drag or friction incident to increasing line pressure. Thus, oscillating valve head 56, which is movable in chamber 48 connected to atmosphere through exhaust port 34, may be oscillating between its selective porting positions relative to working ports 36, 38 by applying relatively low levels of force to the internal actuating mechanisms 52, with the essential design considerations being the appropriate bearing mounting of shaft 54, the extend and finish of the shear-type face seal 68 between sealing members 64, 66 and the extent and finish of the seal between oscillating sealing sleeve 76 and stationary sealing plate 80.

Stationary sealing plate 80 is a circular insert seated in inner end face of housing section 28 (see FIG. 4) and includes first and second circular openings 80a, 80b communicating respectively with the first and second working ports 36, 38. Thus, when the sealing sleeve 76 is coaxial with circular opening 80a, air under pressure flows from air inlet port 32 through shaft 54, radial bore 56a, and through the bores provided by well 561; and the hollow sleeve 76 through opening 800 to the first working port 36. Simultaneously, air from the other side of the cylinder flows back through port 38 through opening 80b into chamber 48 and out exhaust port 34. When the oscillating valve head 56 is oscillated to a position wherein sealing sleeve 76 is coaxial with opening 80b, the air flow path is through circular opening 80b to working port 38. Simultane ously, air from the other side of the cylinder flows back through port 36 through opening 80a into chamber 48 and out exhaust port 34. There will now be described a preferred actuating mechanism for oscillating valve head 56 about the axis of shaft 54 to precisely position the sealing sleeve 76 in registry with the first and second working ports 36, 38, respectively, through corresponding openings 80a, 80b.

Valve actuation is achieved by internal actuating mechanisms 52 (see FIGS. 3 and 6) which includes a arm or escapement plate 82 having a radially extending latch arm 84 which carries an axially extending actuating pin 86 carrying a roller 86a. The latch plate 82 and actuating pin 86 are disposed within the hollow interior 60 of actuating housing section 24 (see FIG. 6). The latch plate is mounted on the reduced diameter end section 54d of the combined air inlet and actuating shaft 54 in any convenient fashion, as by shoulder washer 88 and locknut 90 on an appropriate threaded extension of shaft section 54d. It will be appreciated that limited arcuate motion imparted to actuating pin 86, as shown by the double-headed arrow in FIG. 3 will bring about corresponding selective porting of the oscillating valve head 56. This motion is achieved by the illustrative manually operable snap-action actuating mechanisms, generally designated by the reference numeral 92, and illustrated in FIGS. 9 to 15, inclusive. Working back from the latch plate 82, it is seen to include two circumferentially spaced positioning notches 82a, 82b(see FIGS. 14 and 15). Disposed above and below latch plate 82 are oppositely acting L-shaped latching members 94, 96 which are pivoted on the adjacent face of the intermediate valve housing section 26 at latch pivots 98, 100. Hair spring 102 is mounted on shaft 54 and is operatively connected to the latching members 94, 96 to bias the same in the direction to engage the latch plate 82. Specifically, latching members 94, 96 include triangular latch teeth 94a, 96a which are engaged within positioning notches 82a, 82b, respectively. Cooperating with the latching plate 82 and the latching members 94, 96 are stops 104, 106 mounted on the adjacent face of housing section 26. In the normal rest position of the valve (illustrated in FIG. 14), stop 104 serves to position latch plate 82 with sealing sleeve 76 communicating with the first working port 36 and stop 106 positions latching member 96 in engagement with latch plate 82; and in the operated position (illustrated in FIG. 15), stop 104 serves to position the latching member 94 while stop 106 serves to position the latch plate 82 such that sealing sleeve 76 is in communication with the second working port 38. Actuating pin 86 is loaded in alternation by the opposed springs of snap-action actuating mechanism 92 and when loaded is released for valve actuation by a trigger pin 108 which is positioned in blocking relation alternately with the oppositely directed release jaws 94b, 96b of latching members 94 and 96. The coaction between latch plate 82, latching members 94, 96 and trigger finger 108 will be more fully appreciated as the description proceeds.

The snap-action actuating mechanism 92 which selectively positions the trigger 108 and imparts alternating and abrupt actuating forces to the actuating pin 86 is shown in its normal rest position in FIGS. 9 and 10. It is seen to include a main actuating member or sleeve 110 which is slidably and nonrotatably mounted within actuating housing section 24 by intermediate key 112 on section 24 which is engages within keyway 110a formed in the main actuating member 110. Additional bearings are afforded for actuating member 110 by the provision of an upper mounting head 114 which is removably mounted on housing section 24 and lower mounting sleeve 116 which is removably mounted in the lower face of the housing section 24. Specifically, the mounting head 114 includes an externally threaded cylindrical body 114a which is provided with internal guide surfaces shaped in accordance with the corresponding shape of actuating member 110. Additionally, mounting head 114 includes an intermediately integral nut 11% which facilitates the threaded engagement of the externally threaded body 114a into an appropriately tapped hole in the housing section 24, a spacer ring 117 being interposed therebetween. Still further, mounting head 114 includes a shroud-mounting ring 1140 of triangular cross section which is adapted to engage the lower end of an elastic shroud (not shown) which may be placed over the actuating mechanisms to hide external main spring 118, and seal the mechanism from dirt and moisture. Mounting head 114 is provided with an annular upwardly opening seat 114d to receive the lower end of external main spring 118. The actuating member includes an upper head-mounting bearing section 1l0b which is received within the large diameter section of the guide bore provided by mounting head 114 and a lower head-mounting bearing section 1100 which is received within the guide bore provided by lower mounting sleeve 116. Accordingly, actuating member 110 is guided intermediate its ends by keyway 110a and key 112 and at its upper and lower ends by mounting head 114 and mounting sleeve 116.

Projecting above the actuating member 110 is a depressible plunger 120 which is received within the upper cylindrical section 110d of actuating member 110 and terminating at its upper end in a pushbutton 122. Spaced above the upper end of cylindrical section 110d, plunger 120 carries collar 124 which serves as a mount for spring 118. Within plunger 120 (see FIG. 9), there is provided an internal overtravel plunger spring 126 which is capable of picking up excessive motion applied to pushbutton 122 and plunger 120, plunger 120 being capable of overtravel relative to cylindrical section 110d clue to the provision of an elongated slot 120a transversely therethrough which receives pin 128 mounted on cylindrical section 110d. However, as a practical matter and in normal use, the actuating member 110 and plunger 120 may be considered to be a unitary assembly which moves axially in response to depressing pushbutton 122.

Extending within the upper head-mounting section 1101; there is slidably mounted 'a cylindrical actuating head 130 which is closed at its lower end and open at its upper end. Actuating head 130 is biased downwardly to an extended position relative to bearing section 110!) by an internal actuating spring 132 which bears at one end against the closed bottom end of plunger 120 (see FIG. 9) and at the other end against the closed lower end of actuating head 130. Actuating member 110 is provided with a limit stop and actuating projection 1102 intermediate its end which serve to limit the extended position of actuating head 130 relative to hearing section 110b under the influence of biasing spring 132. In a similar fashion, there is provided a diametrically opposed cylindrical actuating head 134 which is axially aligned with head 130 and has a closed upper end and an open lower end. Actuating head 134 is biased upwardly to an extended position by coil spring 136 which bears at one end against lower mounting sleeve 116. Spring 136 biases head 134 into an extended position determined by the lower flat of limit stop 110e, except for the interposed roller 86a of actuating pin 86. As seen best in FIG. 9, the intermediate portion of actuating member 110 is cut away at l10f such that the actuating pin 86 and its roller 86a can extend between the opposed actuating heads 130, 134 and such that the trigger pin 108, which is mounted on actuating member 110, projects laterally to a position between jaws 94b, 96b of latching members 94, 96 (see FIGS. 14,15).

A typical sequence of operations for the snap-action actuating mechanisms 92 will now be described, reference being made progressively to FIGS. 9-13, inclusive:

In the normal position illustrated in FIGS. 9 and 10 (and in the earlier figures of the drawings), the external main spring 118 biases the actuating member 110 in a direction such that the upper flat on limit stop 1102 bears against the lower closed end of actuating head 130. The lower actuating head 134 bears against the actuating pin 86 which in turn bears against 'stop pin 104 (see FIG. 14), with the trigger pin 108 being in the position designated by notation F10. In this normal rest position, actuating head 134 is spaced from the lower flat of limit stop 110e (see FIG. 10). In order to establish this normal rest position, it will be appreciated that the external main spring 118 is the strongest in the system, the internal overtravel spring 126 is of an intermediate strength and the headactuating springs 132, 136 are the weakest and exert substantially equal and opposite biasing forces on the respective actuating heads I30, 134.

When a downward force is exerted on pushbutton 122, as indicated by the directional arrow in FIG. 11, the effectively unitary assembly of pushbutton 122;, plunger 120 and actuating member 110 move downwardly and both actuating springs 132, 136 are compressed within their respective heads or pistons. Compression of spring 132 occurs incident to contact of head 130 against the head 86a of actuating pin 86 and compression of spring 136 occurs incident to the lower flat of limit stop l10e contacting the actuating head or piston 134 and urging the same downwardly. During this loading of the springs 132, 136, external main spring 118 is compressed, but over travel spring 126 is not unless excessive downward motion is applied to pushbutton 122. The FIG. 11 position shows an intermediate position for the snap-actuating mechanism 92, between that illustrated in FIGS. 10 and 12.

Next, by reference to FIG. 12, it will be seen that the downward stroke of the actuating assembly of pushbutton 122, plunger 120 and actuating member 110 is completed, with the lower ends of the actuating member 110 and head 134 both bottoming on the base of lower mounting member 116. In advance of the FIG. 12 position, trigger pin 108 moves to the intermediate position F11 illustrated in FIG. 14 whereupon latching member 96 is pivoted in the counterclockwise direction about pivot 100 (compare the positions in FIGS. 14 and 15) such that actuating pin 86 is freed to travel through the limited arcuate travel established between stops or pins 104, 106 moving into the position illustrated in FIGS. 12 and 15 wherein the oscillating valve head 56 is in communication with the second working port 38. If further downward pressure is applied to pushbutton 122 from the FIG. 12 position, the overtravel spring 126 is placed in compression and there is relative motion between plunger 120 and actuating member 110.

Referring now to FIG. 13, there is illustrated an intermediate position of the snap-actuating mechanisms 92 as the same is moving from the actuated or operated position of FIG. 12 and prior to return to the normal rest position illustrated in FIG. 10. As seen in FIG. 13 and as illustrated in FIG. 15 by the notation F13, latching member 94 holds the actuating pin 86 in the lower position bearing against lower actuating head 134 with its internal actuating spring 136 in compression. Actuating member 110 has travelled upwardly under the influence of external main spring 118 and upper flat on stop I10e is urging upper actuating head 130 upwardly to place its actuating spring 132 in partial compression. At that appropriate time in the cycle, trigger pin 108 moves upwardly and into contact with the jaw 94b of latching member 94, moving through the intermediate position F13 in FIG. 15, thereby disengaging the escapement mechanism provided by components 82, 94, 96 whereupon the loaded lower actuating spring 136 will again actuate the pin 86 to restore the valve to its normal rest position.

From the foregoing, it will be appreciated that there has been provided in accordance with the present invention a pneumatically actuated valve which can serve as a direct replacement for an electrically controlled valve. Due to the relatively low frictional forces developed incident to operation of the valve in the presence of adequate air seals, it is possible to operate this valve with low forces, notwithstanding line pressures which may reach as high as 150 pounds per square inch. Observations over a wide operating range of working pressures reveal that the force required for valve operation does not appreciably change over such operating range. The valve itself is constructed in a manner such that the forces required for operation more closely approach the low-level forces needed to operate a microswitch. The valve is capable of repeated use over prolonged periods of time with minimum need for servicing, replacement or repair of parts. The simplicity, accuracy, and reliability of this valve which is capable of being snapped from one position to another very quickly and with a minimum of force, satisfies a longstanding need in the pneumatic control industry. The small size and compactness of the valve makes it a feasible component to replace existing microswitch-controlled, solenoid-operated valves and, indeed, the smallness in size makes this valve useful in environments wherein comparable conventional valves would not fit. Further, the valve has an exceptionally large capacity for its size and relatively small actuating forces are required even though the valve openings are comparatively large. Although the invention has been described in connection with the introduction of air at the air inlet port 32, with the air exiting at working ports 36 and 38, it will be appreciated, as is generally by those skilled in the valve art, that this arrangement can be reversed (i.e., air inlet at either of ports 36 or 38).

A latitude of modification, change and substitution is intended in the foregoing disclosure, and in some instances some features of the invention will be employed without a corresponding use of other features. Accordingly, it is appropriate that the appended claims be construed broadly and in a manner consistent with the spirit and scope of the present invention.

What is claimed is:

1. In a valve, a housing having an internal chamber, an elongated combined valve actuating and air inlet shaft disposed within said housing and extending through said chamber, means for journaling said shaft for rotation about its axis, said shaft including an axial bore having an entry end opening through one end of said shaft, means for introducing air under pressure into said entry end of said axial bore, a valve member extending radially within said chamber and operatively connected to said shaft for rotation therewith, means on said housing providing at least one edit port opening into said chamber and a stationary sealing face surrounding said exit port, means on said valve member providing a valve port in communication with said bore and a movable sealing face surrounding said valve port, said stationary and movable sealing faces being at right angles to said shaft axis and contacting to provide a seal as said valve port is moved into and out of registry with said exit port.

2. A valve according to claim 1 including actuating means operatively connected to the other end of said shaft for moving said valve member.

3. A valve according to claim 1 wherein the means for journaling said shaft for rotation includes a face seal about said shaft adjacent said entry end of said bore.

4. A valve according to claim 3 wherein said face seal includes first and second shear sealing faces extending at right angles to said shaft axis, in contact with each other and movable relative to each other in response to rotation of said shaft.

5. A valve according to claim I wherein said valve member includes a sealing sleeve providing said valve port and said movable sealing face, means mounting said sealing sleeve on said valve member for axial movement such that said movable sealing face will bear against said stationary sealing face and a spring biasing said sealing sleeve to urge said movable sealing face against said stationary sealing face.

6. A valve according to claim 5 wherein said movable sealing face is formed on one end of said sealing sleeve, said seal ing sleeve having opposite surfaces dimensioned in relation to each other to achieve substantial pressure equalization on said sealing sleeve whereby the sealing pressure on said seal of said valve member is substantially determined by the bias of said spring.

7. A valve according to claim 1 wherein the means for journaling said shaft includes a ball bearing arranged to take up the axial and radial loading of said shaft developed incident to pressure in said bore and in said radially extending valve member.

8. A valve comprising a housing having an internal chamber, an elongated valve shaft extending through said chamber and journaled in said housing for rotation about the shaft axis, a radially extending valve member disposed within said chamber and operatively connected to said shaft and moving between first and second porting positions in response to oscillating motion of said shaft, means including a bore through said shaft and a bore through said valve member and having an entry port at one end of said shaft and a valve port in said valve member for establishing an air passage through said shaft and valve member terminating at said valve port, a stationary valve plate on said housing including first and second ports in angular spaced relation and opening through a face thereof, the faces of said valve member and said housing being in contact and establishing an air seal in said first and second porting positions of said valve member and an actuating mechanism operatively connected to said shaft for moving said valve member between said first and second porting positions.

9. A valve according to claim 8 wherein said actuating mechanism is of the snap-action type including opposed actuating springs which are loaded and unloaded in alternation.

10. A valve according to claim 8 including means normally porting said internal chamber to atmosphere.

11. An air valve comprising a housing having an internal chamber, a valve head disposed within said chamber, means including a shaft mounting said valve head for oscillating movement between first and second porting positions, means defining a first working port on said housing adapted to communicate with said valve head in said first porting position, means'defining a second working port on said housing adapted to communicate with said valve head in said second porting position, inlet means in communication with the mounting means for said valve head for connecting a pressure source to said valve head for transfer to one or the other of said working ports, means for porting said internal chamber to atmosphere, a face seal on said shaft and on said housing exposed to said pressure source at one side and to atmosphere at the other side and actuating means for oscillating said valve head between said first and second porting positions.

12. A valve according to claim 11 wherein said inlet means is connected to one end of said shaft and said actuating means is operatively connected to the other end of said shaft.

13. A valve according to claim 11 wherein the means mounting said shaft for oscillating movement includes a face seal about said shaft.

14. A valve according to claim 13 wherein said face seal includes first and second annular sealing faces extending at right angles to said shaft, in contact with each other and movable relative to each other in response to oscillating movement of said shaft.

15. A valve according to claim 11 wherein said valve operatively includes a sealing sleeve providing a valve port and a movable sealing face, means mounting said sealing sleeve on said valve head for axial movement and a spring biasing said sealing sleeve outwardly relative to said valve head.

16. A valve according to claim 15 wherein said movable sealing face is formed on one end of said sealing sleeve, said sealing sleeve having opposite end faces dimensioned in relation to each other to achieve substantial pressure equalization on said sealing sleeve.

17. A valve according to claim 11 wherein the means for mounting said shaft includes a ball bearing arranged to take up the axial and radial loading of said shaft developed incident to pressure therein and in said radially extending valve head.

18. A valve having a housing with a plurality of ports therein for the passage of fluid into and out of said valve comprising actuating means movable from a first position to a second position; control means for controlling the passage of fluid between said ports, said control means including a first latch member movably connected to said housing, a valve movable relative to said housing between first and second porting posi- Eli tions and operatively connected to said ports, said valve being effective to connect and disconnect said ports in its first and second porting positions respectively, and means operatively connected to said first latch member and effective to urge it into engagement with said valve to hold said valve in a given one of said porting positions; means operatively connected to said actuating means and to said first latch member and effective to move said first latch member out of holding engagement with said valve at a predetermined position of said acmember effective to move said second latch member out of holding engagement with said valve at a predetermined position of said actuating means, and second snap means operatively connected to said valve and effective to snap it to the first of said porting positions when said second latch member is moved out of holding engagement therewith.

20. A valve according to claim 18 in which said means effective to release said first latch member includes a member connected to and extending outwardly from said actuating means a sufficient distance to engage said first latch member as said actuating means moves to said second position.

21. A valve according to claim 18 in which said snap means includes an upper spring operatively connected to said actuating means and to said valve, said upper spring being positioned so as to be placed in compression by the movement of said actuating means from said first position to said second position thereby to place said valve under actuating pressure, whereupon when said first latch member is released, said valve is caused to snap to a second position by said upper spring.

22. A valve according to claim 19 in which said means to restore said valve to the original porting position on the release of said second latch member includes a lower spring operatively connected to said actuating means and to said valve, said lower spring being positioned so as to be placed in compression by the movement of said actuating means from said first position to said second position thereby to place said valve under actuating pressure when said valve is in said second porting position whereupon when said second latch member is released, said valve is caused to snap to the original porting position by said lower spring.

23. In a valve, a housing having an internal chamber, an elongated shaft disposed within said housing and extending through said chamber, means for journaling said shaft for rotation about its axis, said shaft including an axial bore having an entry end opening through one end of said shaft, a valve member extending radially within said chamber and operatively connected to said shaft for rotation therewith, means on Said housing providing at least one port opening into said chamber and a stationary sealing face surrounding said one port, means on said valve member providing a valve port in communication with said bore and a movable sealing face surrounding said valve port, said stationary and movable sealing faces being at right angles to said shaft axis and contacting to provide a seal as said valve port is moved into and out of registry with said one port.

t l i i 

1. In a valve, a housing having an internal chamber, an elongated combined valve actuating and air inlet shaft disposed within said housing and extending through said chamber, means for journaling said shaft for rotation about its axis, said shaft including an axial bore having an entry end opening through one end of said shaft, means for introducing air under pressure into said entry end of said axial bore, a valve member extending radially within said chamber and operatively connected to said shaft for rotation therewith, means on said housing providing at least one exit port opening into said chamber and a stationary sealing face surrounding said exit port, means on said valve member providing a valve port in communication with said bore and a movable sealing face surrounding said valve port, said stationary and movable sealing faces being at right angles to said shaft axis and contacting to provide a seal as said valve port is moved into and out of registry with said exit port.
 2. A valve according to claim 1 including actuating means operatively connected to the other end of said shaft for moving said valve member.
 3. A valve according to claim 1 wherein the means for journaling said shaft for rotation includes a face seal about said shaft adjacent said entry end of said bore.
 4. A valve according to claim 3 wherein said face seal includes first and second shear sealing faces extending at right angles to said shaft axis, in contact with each other and movable relative to each other in response to rotation of said shaft.
 5. A valve according to claim 1 wherein said valve member includes a sealing sleeve providing said valve port and said movable sealing face, means mounting said sealing sleeve on said valve member for axial movement such that said movable sealing face will bear against said stationary sealing face and a spring biasing said sealing sleeve to urge said movable sealing face against said stationary sealing face.
 6. A valve according to claim 5 wherein said movable sealing face is formed on one end of said sealing sleeve, said sealing sleeve having opposite surfaces dimensioned in relation to each other to achieve substantial pressure equalization on said sealing sleeve whereby the sealing pressure on said seal of said valve member is substantially determined by the bias of said spring.
 7. A valve according to claim 1 wherein the means for journaling said shaft includes a ball bearing arranged to take up the axial and radial loading of said shaft developed incident to pressure in said bore and in said radially extending valve member.
 8. A valve comprising a housing having an internal chamber, an elongated valve shaft extending through said chamber and journaled in said housing for rotation about the shaft axis, a radially extending valve member disposed within said chamber and operatively connected to said shaft and moving between first and second porting positions in response to oscillating motion of said shaft, means including a bore through said shaft and a bore through said valve member and having an entry port at one end of said shaft and a valve port in said valve member for establishing an air passage through said shaft and valve member terminating at said valve port, a stationary valve plate on said housing including first and second ports in angular spaced relation and opening through a face thereof, the faces of said valve member and said housing being in contact and establishing an air seal in said first and second porting positions of said valve member and an actuating mechanism operatively connected tO said shaft for moving said valve member between said first and second porting positions.
 9. A valve according to claim 8 wherein said actuating mechanism is of the snap-action type including opposed actuating springs which are loaded and unloaded in alternation.
 10. A valve according to claim 8 including means normally porting said internal chamber to atmosphere.
 11. An air valve comprising a housing having an internal chamber, a valve head disposed within said chamber, means including a shaft mounting said valve head for oscillating movement between first and second porting positions, means defining a first working port on said housing adapted to communicate with said valve head in said first porting position, means defining a second working port on said housing adapted to communicate with said valve head in said second porting position, inlet means in communication with the mounting means for said valve head for connecting a pressure source to said valve head for transfer to one or the other of said working ports, means for porting said internal chamber to atmosphere, a face seal on said shaft and on said housing exposed to said pressure source at one side and to atmosphere at the other side and actuating means for oscillating said valve head between said first and second porting positions.
 12. A valve according to claim 11 wherein said inlet means is connected to one end of said shaft and said actuating means is operatively connected to the other end of said shaft.
 13. A valve according to claim 11 wherein the means mounting said shaft for oscillating movement includes a face seal about said shaft.
 14. A valve according to claim 13 wherein said face seal includes first and second annular sealing faces extending at right angles to said shaft, in contact with each other and movable relative to each other in response to oscillating movement of said shaft.
 15. A valve according to claim 11 wherein said valve operatively includes a sealing sleeve providing a valve port and a movable sealing face, means mounting said sealing sleeve on said valve head for axial movement and a spring biasing said sealing sleeve outwardly relative to said valve head.
 16. A valve according to claim 15 wherein said movable sealing face is formed on one end of said sealing sleeve, said sealing sleeve having opposite end faces dimensioned in relation to each other to achieve substantial pressure equalization on said sealing sleeve.
 17. A valve according to claim 11 wherein the means for mounting said shaft includes a ball bearing arranged to take up the axial and radial loading of said shaft developed incident to pressure therein and in said radially extending valve head.
 18. A valve having a housing with a plurality of ports therein for the passage of fluid into and out of said valve comprising actuating means movable from a first position to a second position; control means for controlling the passage of fluid between said ports, said control means including a first latch member movably connected to said housing, a valve movable relative to said housing between first and second porting positions and operatively connected to said ports, said valve being effective to connect and disconnect said ports in its first and second porting positions respectively, and means operatively connected to said first latch member and effective to urge it into engagement with said valve to hold said valve in a given one of said porting positions; means operatively connected to said actuating means and to said first latch member and effective to move said first latch member out of holding engagement with said valve at a predetermined position of said actuating means; and first snap means operatively connected to said valve and effective to snap it to the other one of said porting positions when said first latch member is moved out of holding engagement therewith.
 19. A valve according to claim 18 including a second latch member movably connected to said housing, means operatively conneCted to said second latch member and effective to urge it into engagement with said valve to hold said valve in a given one of said porting positions, means operatively connected to said actuating means and to said second latch member effective to move said second latch member out of holding engagement with said valve at a predetermined position of said actuating means, and second snap means operatively connected to said valve and effective to snap it to the first of said porting positions when said second latch member is moved out of holding engagement therewith.
 20. A valve according to claim 18 in which said means effective to release said first latch member includes a member connected to and extending outwardly from said actuating means a sufficient distance to engage said first latch member as said actuating means moves to said second position.
 21. A valve according to claim 18 in which said snap means includes an upper spring operatively connected to said actuating means and to said valve, said upper spring being positioned so as to be placed in compression by the movement of said actuating means from said first position to said second position thereby to place said valve under actuating pressure, whereupon when said first latch member is released, said valve is caused to snap to a second position by said upper spring.
 22. A valve according to claim 19 in which said means to restore said valve to the original porting position on the release of said second latch member includes a lower spring operatively connected to said actuating means and to said valve, said lower spring being positioned so as to be placed in compression by the movement of said actuating means from said first position to said second position thereby to place said valve under actuating pressure when said valve is in said second porting position whereupon when said second latch member is released, said valve is caused to snap to the original porting position by said lower spring.
 23. In a valve, a housing having an internal chamber, an elongated shaft disposed within said housing and extending through said chamber, means for journaling said shaft for rotation about its axis, said shaft including an axial bore having an entry end opening through one end of said shaft, a valve member extending radially within said chamber and operatively connected to said shaft for rotation therewith, means on said housing providing at least one port opening into said chamber and a stationary sealing face surrounding said one port, means on said valve member providing a valve port in communication with said bore and a movable sealing face surrounding said valve port, said stationary and movable sealing faces being at right angles to said shaft axis and contacting to provide a seal as said valve port is moved into and out of registry with said one port. 